Speed ratio control system and method for a continuously variable transmission for a vehicle

ABSTRACT

A speed ratio control system of a continuously variable transmission for a vehicle is provided, wherein a speed ratio is feedback-controlled in association with a deviation between a target and a measured value, so that the speed ratio can be continuously varied and adjusted. A gain of feedback control or shift speed is utilized, which has been constant or accurately determined, and the gain of feedback control or shift speed is optimally set in accordance with the feedback control, so as to obtain a continuously variable transmission which has high response characteristics and stability.

This is a Division of application Ser. No. 06/867,443 filed May 28,1986, now U.S. Pat. No. 4,999,774.

BACKGROUND OF THE INVENTION

This invention relates to a speed ratio control system of a continuouslyvariable transmission for a vehicle, wherein a speed ratio isfeedback-controlled in association with a deviation between a target anda measured value, so that the speed ratio can be continuously varied andadjusted, more particularly this invention relates to improvements in aspeed ratio control system of a continuously variable transmission for avehicle, wherein better shift characteristics can be obtained byimproving a shift speed or a gain of feedback control.

In general, continuously variable transmission mechanisms includeV-shaped pulley devices, each including a stationary pulley and amovable pulley, and each having an effective diameter which can bevaried by hydraulic servo devices. These V-shaped pulleys are providedon input shafts and output shafts respectively, so that rotation of theinput shaft can be shifted in the continuously variable manner andtransmitted to the output shaft by a driving belt extending between theV-shaped pulley devices. Normally, an oil flowrate to the hydraulicservo device on the input side is varied by a flow control valve,whereby the effective diameter of the V-shaped pulley device on theinput side is forcibly changed. On the other hand, hydraulic pressure ofthe hydraulic servo device on the output side is varied by a pressurecontrol valve to thereby follow the change of the effective diameter ofthe V-shaped pulley device on the input side, so that the driving beltwill not slip in transmitting the torque.

As compared with automatic transmission mechanisms, which consist ofso-called torque converters with groups of planetary gear units, theabove-described continuously variable transmission mechanisms areadvantageous in that abrupt changes in driving force during running ofthe vehicle are reduced, shift shocks are low, and the fuel consumptionrate is good. In recent years, there is an increased demand for furtherimprovements in continuously variable transmission mechanisms.

The speed ratio control of continuously variable transmissions hasheretofore been performed as described below. First, a target value(normally, a target rotational speed Nin° or a target speed ratio e°) iscalculated, a deviation D=Nin°-Nin (or D=e°-e) is calculated, and, inassociation with this deviation D, an oil flowrate Q (=a control voltageVin of the flow control valve, being commensurate to the oil flowrate Q)to the hydraulic servo device on the input side is calculated through anequation Vin =K·D. K is a feedback gain and has heretofore been set at aconstant value. Furthermore, this control voltage Vin has determined theoil flowrate at the flow control valve, and in turn, determined theshift speed. As a consequence, heretofore, the feedback gain K has beenset at a constant value, and, the shift speed has been also inevitablydetermined in association with a deviation between a target value and ameasured value.

However, the conventional control described above presents adisadvantage in that it may not satisfactorily smoothly transfer themeasured value to the target value during the transitional period andstably maintain the continuously variable transmission at the targetvalue at steady state.

SUMMARY OF THE INVENTION

The present invention was developed to obviate the above-describeddisadvantages of the prior art. Accordingly, it is an object of thepresent invention to provide a speed ratio control system for acontinuously variable transmission, wherein, a gain of feedback controlor shift speed is improved. The gain, is optimally set in associationwith the feedback control, so as to obtain a continuously variabletransmission with good response characteristics and stability.

To achieve the above-described object, a first aspect of the presentinvention contemplates that, in a speed ratio control system for acontinuously variable transmission, wherein a speed ratio isfeedback-controlled in association with a deviation between a target anda measured value, so that the speed ratio can be continuously varied andadjusted, the system is provided with at least means for setting atarget shift speed in association with the rotating conditions of anengine and means for setting a gain of the feedback control inassociation with the target shift speed.

In a specific form of the first aspect of the present invention,information to indicate the rotating conditions of the engine couldinclude an engine rotational speed, an engine torque, a throttleopening, negative pressure of an intake manifold and engine coolingwater temperature, so that the target shift speed can be precisely set.

In another specific form of the first aspect of the present invention, again of the feedback control is set to be in proportion to the targetshift speed, so that the gain of the feedback control can be preciselyset.

In another specific form of the first aspect of the present invention, again of the feedback control is separately set, depending on a positiveor a negative sign of a shift speed, i.e. an increase or a decrease inspeed, so that poor response, resulting from a difference incharacteristics due to the oil flow direction in the flow control valveis obviated.

A second aspect of the present invention contemplates that, in a speedratio control system of a continuously variable transmission, wherein aspeed ratio is feedback-controlled in association with a deviationbetween target and measured values, so that the speed ratio can becontinuously varied and adjusted, the system is provided with means fordetecting the magnitude of the deviation between the target and themeasured values and means for varying a gain of the feedback control,depending on whether the deviation is large or small.

In a third aspect of the present invention, the speed ratio isfeedback-controlled in association with a deviation between target andmeasured values, so that the speed ratio can be continuously varied andadjusted. The system is provided with means for detecting whether thedeviation between the target and the measured values is small, and meansfor setting a target shift speed in association with the deviation whenthe deviation is small.

In a specific form of a third aspect of the present invention, thetarget shift speed is set in proportion to the deviation, so that thetarget shift speed can be precisely set.

In a fourth aspect of the present invention, the system is provided withat least means for setting a target shift speed in accordance with therotating conditions of the engine, means for detecting an actual shiftspeed and means for reflecting a signal associated with a deviationbetween the target shift speed and the actual shift speed in amanipulated variable signal associated with the deviation between thetarget value and the measured value in the feedback control.

In a specific form of the fourth aspect of the present invention,information to indicate the rotating condition of the engine couldinclude an engine rotational speed, an engine torque, a throttleopening, negative pressure of an intake manifold and engine coolingwater temperature.

One of the specific problems in the prior art, is that the measuredvalue (the result of feedback control=controlled variable) becomesvibratory. One of the causes is the flow control valve. Thecharacteristics of the flow control valve which correspond to one of thefinal controlling elements is normally shown in FIG. 5. As shown in aportion A in FIG. 5, the flowrate characteristics to a control voltage(control current) is steep in the rising portion, and in the extremecase, substantially ON-OFF control is effected. As a consequence, it isdifficult to effect accurate control in a very small flowrate.

In the first aspect of the present invention, a feedback gain is variedand adjusted in association with a shift speed, so that, when the shiftspeed is slow, i.e. the change in flowrate is small, the feedback gainof the speed ratio control can be made small so as to suppress thevibrations of an output.

In the second aspect of the present invention, the magnitude of adeviation between the target and the measured values is detected, and,when the deviation is large (during shifting), the feedback gain is setat a large value so as to improve response, whereas, when the deviationis small (during running at a constant speed), the feedback gain is setat a small value so as to improve stability.

In the third aspect of the present invention, the deviation between thetarget and the measured values is detected. When the deviation is small,a shift speed, commensurate to the deviation, is set. When the deviationis large, the feedback control can be effected in such a manner that ashift speed is adopted in which the consumption rate, response and thelike are important. When the deviation is small, the feedback controlcan be stably effected at a shift speed commensurate to the deviation.Particularly, this third aspect of the present invention is effective insetting a comparative value (setting shift speeds) in a conventionalfeedback control.

On the other hand, as aforesaid, the control has heretofore beeneffected according to the equation of Vin=K·D for example, whereby, evenif a shift demand is issued, unless an absolute value |Nin°-Nin| of thedeviation increases to some extent after a lapse of some period of time,a control voltage Vin (manipulated variable) does not increase, thuscreating a poor response. According to the fourth aspect of the presentinvention, for example, through an equation of Vin=Kp (Nin°-Nin)+Kd(dNin°-dNin), a signal associated with a deviation between a targetshift speed dNin° and an actual shift speed dNin is reflected in amanipulated variable associated with a deviation between the target andthe measured values, so that, upon issuing the shift demand, the targetshift speed dNin° is immediately varied and the control voltage Vin canbe rapidly generated because of the term in the right member of theabove-mentioned equation. Thus, the response can be improvedaccordingly.

BRIEF DESCRIPTION OF THE DRAWINGS

The exact nature of this invention, as well as other objects andadvantages thereof, will be readily apparent from the description of theinvention which follows, taken in conjunction with the accompanyingdrawings, in which like reference characters designate the same orsimilar elements, and wherein:

FIGS. 1 to 4 are block diagrams showing the technical aspects of thespeed ratio control system of the continuously variable transmissionsfor a vehicle according to the present invention, respectively;

FIG. 5 is a chart showing the characteristics of the flow control valve;

FIG. 6 is a schematic block diagram showing the continuously variabletransmission for a vehicle embodying the present invention;

FIG. 7 is a chart showing the relationship between an intake throttleopening and a target input rotational speed in explanation of theadvantage of introducing the idea of the comparative value;

FIG. 8 is a chart showing the relationship between a target inputrotational speed, an actual input rotational speed and a comparativerotational speed, along the time axis;

FIG. 9 is a block diagram regarding the speed ratio control used in thesystem in the above-described embodiment;

FIG. 10(A) and 10(B) are a flow chart showing the routine of the speedratio control as a whole; and

FIG. 11(A) and 11(B) are charts showing the conditions of the responseregarding the speed ratio control in the above-described embodiment andin the conventional example, respectively.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Detailed description will hereunder be given of one embodiment of thepresent invention with reference to the accompanying drawings.

FIG. 6 shows the general continuously variable transmission system for avehicle, to which the speed ratio control system according to thepresent invention is applied.

Referring to the drawing, an output shaft 2 of an internal combustionengine E/G is connected to a continuously variable transmission(hereinafter referred to as a "CVT") through a fluid coupling 4. ThisCVT includes V-shaped pulleys 10 and 14 positioned on input and outputshafts 6 and 8, respectively. V-shaped pulley 10 includes a stationarypulley 11 and a movable pulley 12. V-shaped pulley 14 includes astationary pulley 15 and a movable pulley 16. The stationary pulley 11on the input side is fixed to the input shaft 6 and the movable pulley12 on the input side is axially movably coupled to the input shaft 6through splines, ball bearings or the like. Similarly, the stationarypulley 15 on the output side is fixed to the output shaft 8 and themovable pulley 16 on the output side iss axially movably coupled to theoutput shaft 8 through splines, ball bearings or the like. Pressurereceiving areas of the respective movable pulleys 12 and 16 are set suchthat the pressure receiving area on the input pulley is larger than thepressure receiving area on the output pulley. A forcible change in theeffective diameter, to vary the speed ratio, can thus be made on theinput side. On the input and the output sides, movement in the axialdirections of the movable pulleys 12 and 16, in relation to thestationary pulleys, is made opposite to each other, so that a drivingbelt 18 is constantly guided around the input and the output shaft 6 and8 at right angles to the lengths of shafts 6 and 8.

Opposed surfaces of the stationary pulleys 11, 15 and the movablepulleys 12, 16 are tapered with distances between the opposed surfacesincreasing radially outwardly. The driving belt 18 is of a generalisosceles trapezoid shape in cross section. The contact positionsbetween driving belt 18 and the pulley surfaces continuously varies asthe distance between stationary and movable pulleys of the respectiveV-shaped pulley devices 10 and 14 varies. When the contact positions ofthe driving belt 18 in the V-shaped pulley device 10 on the input sidemove radially outwardly, the contact positions of the driving belt 18 inthe V-shaped pulley device on the output side move radially inwardly,and the speed ratio e of the CVT (e=Nout (the rotational speed of theoutput shaft 8)/Nin (the rotational speed of the input shaft))increases, whereas, in the opposite case, the speed ratio e decreases.

A driving force of the output shaft 8 is transmitted to a traction wheelby a planetary gear unit which switches the forward and reversedirections of movement, gears for speed decrease, differential gears andthe like which are not shown.

A throttle opening sensor 19 detects an opening Ath of a throttle valve(not shown) of the intake system. An accelerator pedal (not shown) isconnected to the throttle valve of the intake system. The output fromthe engine E/G can therefore be a desired function of a value indicativeof the depression of the accelerator pedal.

The rotational angle sensors 20 and 21 on the input and output sides ofthe CVT detect the angles of rotation of the pulleys 11 and 16,respectively. As a result, the input shaft speed and the output shaftspeed (rpm) are detected.

A pressure control valve 24 controls a spill value of oil delivered froma reservoir 26 through an oil line 27 by an oil pump 25 to an oil line28, to thereby regulate a line pressure PL of an oil line 29. Ahydraulic servo device of the movable pulley 16 on the output side isfed with the line pressure PL through the oil line 29.

A flow control valve 30 controls oil flowing into and flowing out of themovable pulley 12 on the input side. To maintain the speed ratio e ofthe CVT at a constant value, an oil line 33 is disconnected from a linepressure oil line 31, which branches from the oil line 29, and a drainoil line 32. As a result, the axial position of the movable pulley 12 onthe input side is held constant and the speed ratio e is maintained at aconstant value. To increase the speed ratio e, oil is fed into thehydraulic servo device of the movable pulley 12 on the input side, fromthe line pressure oil line 31, through the oil line 33. As a result, theclamping force between the pulleys 11 and 12 on the input sideincreases, whereby the distance between pulleys 11 and 12 decreases andthe contact positions of the driving belt 18 on the surfaces of thepulleys 11 and 12 on the input side move radially outwardly. Thus, thespeed ratio e increases. On the other hand, to decrease the speed ratioe, oil in the hydraulic servo device of the movable pulley 12 on theinput side is drained through the oil drain line 32, whereby theclamping force between the pulleys 11 and 12 on the input sidedecreases. The oil pressure in the oil line 33 is less than the linepressure PL. However, as described above, the pressure receiving area ofthe hydraulic servo device of the movable pulley 12 on the input side isset at a value larger then that of the pressure receiving area of thehydraulic servo device of the movable pulley 16 on the output side, sothat the clamping force between the pulleys 11 and 12 can be larger thanthe clamping force between the pulleys 15 and 16 on the output side.

The clamping force of the pulleys 11 and 12 on the input side is variedby the flow control valve 30, whereby the effective diameter between thepulleys 11 and 12 on the input side is changed. On the other hand, theline pressure PL is regulated by the pressure control valve 24, wherebythe clamping force is generated between the pulleys 15 and 16 on theoutput side so that following the change in the effective diameter oninput side, driving belt 18 can transfer the torque from the input tothe output without slip.

An electronic control unit 38 includes a D/A converter 40, an inputinterface 41, an A/D converter 42, a CPU 43, a RAM 44 and a ROM 45,which are connected to each other by an address data bus 39. An analogueoutput from the throttle opening sensor 19 is delivered to the A/Dconverter 42, and pulses from the rotational angle sensors 20 and 21 aredelivered to the input interface 41. The control voltages Vin and Voutto the flow control valve 30 and the pressure control valve 24 aredelivered from the D/A converter 40 through amplifiers 50 and 51respectively.

The basic principle of the control of this embodiment will now bedescribed with reference to FIGS. 7 and 8.

In FIG. 7, the throttle opening Ath of the intake system is given as anabscissa and the target input rotational speed Nin° (a target enginerotational speed Ne°) is given as an ordinate. As described in detail inJapanese Patent Application No. 67362/1982 and the like, Ath-Nin° is setso that an output demanded can be obtained at the minimum fuelconsumption rate. FIG. 8 shows a change per unit time duration of theinput rotational speed Nin and the like of the CVT. When the targetinput rotational speed Nin° is changed too Nin° 1 in a stepped manner ata time t1, if Nin is controlled, utilizing Nin° 1 as the direct targetvalue, then, when Nin approaches the target value Nin° 1, a change perunit time duration decreases. This is disadvantageous because it causesa delay in reaching the target value. To overcome this delay, in oneadvantageous embodiment of this invention, comparative rotational speedsNin' are set in addition to the target input rotational speed Nin°, andNin is feedback-controlled, utilizing Nin' as the target values. Thecomparative rotational speeds Nin' are set as the ideal locus of Nin,i.e. the ideal locus of the shift speeds until Nin reaches the propertarget value Nin°. Optimal values for Nin' are selected experimentally,using theorectical formulas and the like, in association with the enginerotating conditions and in consideration of the various controlperformances. (In a third part of the present invention, when adeviation between the target input rotational speed and the real inputrotational speed is small, this locus is determined in association withthis deviation). Additionally, the feedback control of comparativevalues is described in detail in Japanese Patent Laid-Open (Kokai) No.26656/1984.

FIG. 9 is the general block diagram showing the control system in theabove-described embodiment of this system. The outline of the controlsystem will first be described with reference to FIG. 9. In block 55,the target input rotational speed Nin° is determined as a function ofthe throttle opening Ath, on the basis of the throttle opening Athdetected by the throttle opening sensor 19. In block 57, the targetinput rotational speed Nin° and the actual input rotational speed Ninare inputted and the comparative rotational speed Nin' (being set inassociation with the target shift speed dNin°) is calculated. In block59, the control voltage Vin to the flow control valve 30 is determinedon the basis of the comparative rotational speed Nin' and this controlvoltage Vin is delivered to the flow control valve 30 through anamplifier 50. As the result, a flowrate Q to the hydraulic servo deviceon the input side through the flow control valve 30 is varied, wherebythe speed ratio e of the CVT, namely, Nin is varied. More specifically,Nin is feedback-controlled, utilizing the comparative rotational speedNin' as new target value. An additional detailed description will begiven later of the calculations in blocks 57 and 59.

In block 60, an engine output torque Te is calculated as a function ofthe throttle opening Ath and the input rotational speed Nin. In block61, the control voltage Vout of the pressure control valve is determinedas a function g of the engine output torque Te, and the input and outputrotational speeds Nin and Nout of the CVT. This control voltage Vout isdelivered to the pressure control valve 24 through an amplifier 51 forthe pressure control valve. As the result, the line pressure PL ismaintained at the minimum value required to transfer the torque by thedriving belt 18 without slip. Thus, a loss of the driving force due toan excessive line pressure and a lowered durability of the belt can beavoided.

Details of calculations in the blocks 57 and 59 will be describedhereinunder with reference to the flow chart shown in FIGS. 10(A) and10(B).

Firstly, in Step 102, the target shift speed dNin° is determined bycalculating as a function f₁, or refering to a map, on the basis of thethrottle opening Ath, the CVT input rotational speed Nin, a vehiclespeed V and the like. Additionally, the target shift speed dNin° may bedetermined on the basis of the engine output torque Te, negativepressure of the intake manifold, the engine rotational speed Ne, thespeed ratio e and the like, in addition to the above-mentioned factorsor in place of the above-mentioned factors. Prior to warm-up of theengine, dNin° may be suitably corrected by the engine cooling watertemperature, the CVT oil temperature and the like. In any case, thetarget shift speed dNin° is preferably based on the engine rotatingconditions. However, there is no restriction on the relationship used todetermine the target shift speed dNin°.

Subsequently, in Steps 104-110, limits of the maximum value and theminimum value are applied to the target shift speed dNin°, whereby thevalue of dNin° must be more than C1 and less than C2.

In Step 112, an absolute value of a difference between the measuredinput rotational speed Nin and the target input rotational speed Nin°,i.e. an absolute value of the deviation D, and a constant C3 arecompared in magnitude. When the deviation D is larger than the constantC3, namely, during shifting for example, dNin° sought in Step 102 isused as it is. However, when the deviation D is smaller than theconstant C3, namely, during running at a constant speed for example, theroutine proceeds to Step 114 and the following equation is set, so thatthe target shift speed dNin° is brought into proportion to the deviation|Nin-Nin°|.

    dNin°=C4×dNin°×|Nin-Nin°.vertline.(1)

where C4 is a constant.

In Step 116, Nin and Nin° are compared with each other, and a judgmentis made to accelerate or decelerate. If acceleration is adopted, theroutine proceeds to Step 118 and the comparative rotational speed Nin'is set as shown in the following equation (2). When deceleration isadopted, the routine proceeds to Step 120, and Nin' is set as shown inthe following equation (3).

    Nin'=Nin'+dNin°×t                             (2)

    Nin'=Nin'-dNin°×t                             (3)

where t is a computing cycle.

This Step successively corrects the comparative rotational speeds Nin'into values (locus) commensurate with the target shift speed dNin° withevery computing cycle t.

In Steps 122, 124 and Steps 126, 128, to prevent the comparativerotational speed Nin' from becoming excessively large because ofmalfunctions and the like, or from becoming excessively small, thelimits shown in the following formulae are applied with everyacceleration or deceleration. When Nin<Nin°,

    Nin'≦Nin°+C5                                 (4)

When Nin≧Nin°,

    Nin'≧Nin°-C6                                 (5)

where C5 and C6 are constants.

In Step 130, the feedback gain Kp is brought into proportion to thetarget shift speed dNin° as shown in the following equation.

    Kp=C7×Kpo×dNin°                         (6)

where C7 is a constant and Kpo is a basic feedback gain.

In Step 132, a judgment is made as to whether the target shift speeddNin° is larger or smaller than a predetermined value C8. When thetarget shift speed dNin° is smaller than the predetermined value C8, thefeedback gain is set at a constant C9. Since, in Step 130, the feedbackgain Kp is brought into proportion to the target shift speed dNin°, inthis Step, when the target shift speed dNin° is extremely small, duringrunning at a constant speed for example, the feedback gain Kpdisadvantageously becomes excessively small, so the minimum value limitis applied.

In Step 136, the measured value Nin and the target input rotationalspeed Nin° are compared again, a change in gain is performed with everyacceleration (oil flows out of the hydraulic servo device on the inputside) and deceleration (oil flows thereinto). In this embodiment, inStep 138, the gain is multiplied by C10 during acceleration.

In Step 140, an absolute value of a deviation between the inputrotational speed Nin, which has been measured again, and the targetinput rotational speed Nin°, is compared with a constant C11, and, whenthe absolute value is larger than the constant C11 (this occurs when thedeviation is large during shifting and so forth) to quicken theresponding speed, the routine goes to Step 142, where the feedback gainKp is multiplied by C12.

In Step 144, the control voltage Vin of the flow control valve iscalculated using the following equation.

    Vin=Kp(Nin-Nin')+Kd(dNin-dNin°)                     (7)

where Kd is a constant and dNin is a differentiated value of themeasured value Nin. Additionally, when decelerating, dNin in equation(7) is negative value. In this Step, on the basis of the above-describedtheory, a signal proportionate to the deviation between the target shiftspeed dNin° and the actual shift speed dNin is applied to the controlvoltage Vin of the flow control valve. Namely, upon a demand for ashift, the target shift speed is changed to dNin°. As a result, thechange is immediately reflected as a change of the control voltage Vinby the second term of the right member of equation (7), so that theresponse can be improved accordingly.

FIG. 11(A) shows the responses in the above-described embodiment. FIG.11(B) shows the responses in the conventional example. As is apparent,these drawings confirm that the embodiment described above improves thestability, and the response.

Additionally, in the above-described embodiment, as the subject of thetarget value or the measured value, the input rotational speed Nin hasbeen used. However, according to the present invention, the subject ofthe target value or the measured value need not necessarily berestricted to the input rotational speed Nin. For example, the speedratio e of the continuously variable transmission can be used to set atarget value.

Furthermore, in the above-described embodiment, in the equation (7), thecontrol voltage Vin is directly calculated. However, according to thepresent invention, various corrections can be made to take into accountthe non-linearity of the continuously variable transmission in theequation.

Obviously, numerous modifications and variations of the presentinvention are possible in light of the above teachings. It is thereforeto be understood that while the preferred embodiment of the presentinvention has been described, the invention is not limited thereto, andmay be otherwise embodied within the scope of the following claims.

What is claimed is:
 1. A speed ratio control system for a continuouslyvariable transmission for a vehicle, wherein a speed ratio is feed-backcontrolled in association with a deviation between a target value and ameasured value, the target value and the measured value both selectedfrom one of a group consisting of a speed ratio, an input rotation ofthe continuously variable transmission and an engine speed, whereby saidspeed ratio can be continuously varied and adjusted, said systemcomprising:means for detecting a magnitude of a deviation between thetarget value and the measured valve; means for adjusting a variable gainof a feedback control based on a size of said deviation; and means forusing said variable gain to determine the size of the adjustment of thespeed ratio that is applied by means of a control voltage to a flowcontrol valve of the continuously variable transmission.
 2. A speedratio control system for a continuously variable transmission for avehicle, wherein a speed ratio is feed-back controlled whereby saidspeed ratio can be continuously varied and adjusted, said systemcomprising:means for setting a target shift speed; means for detectingwhether a magnitude of a deviation between a target value and a measuredvalve is smaller than a predetermined value, the target value and themeasured value both selected from one of a group consisting of a speedratio, an input rotation of the continuously variable transmission andan engine speed; means for adjusting said target shift speed inassociation with said deviation when said deviation is smaller than saidpredetermined value; and means for using said target shift speed todetermine the size of the adjustment of the speed ratio that is appliedby means of a control voltage to a flow control valve of thecontinuously variable transmission.
 3. The speed ratio control systemset forth in claim 2, wherein said target shift speed is set inproportion to said deviation.